Scroll compressor

Description

BACKGROUND OF THE INVENTION

[0001] The present invention relates to a scroll type compressor according to the preamble of claim 1 for compressing refrigerant, which is a part of a refrigerant circuit of an air conditioner.

[0002] In such a scroll type compressor, the housing includes a fixed scroll member, which has a fixed base plate and a fixed scroll wall that extends from the fixed base plate, and a movable scroll member, which has a movable base plate and a movable scroll wall that extends from the movable base plate and engages with the fixed scroll wall. By the orbital motion of the movable scroll member with the self-rotation thereof being blocked, compression chambers defined between the fixed scroll wall and the movable scroll wall move radially and inwardly to progressively reduce their volumes, thus compressing refrigerant gas.

[0003] Recently, carbon dioxide has generally been employed as refrigerant for the refrigerant circuit. Pressure in the refrigerant circuit when employing carbon dioxide as refrigerant is higher than that when employing fluorocarbon as refrigerant. Accordingly, in a scroll type compressor, unusually large thrust force is applied to the movable scroll member based upon the high pressure in the compression chamber. Then, the movable scroll member slides under the hard condition, and durability of the scroll type compressor is deteriorated.

[0004] In order to solve such problems, according to pages 4 and 5, and figure 1 of JP-A-2000-249086, the movable scroll member forms a recess on its back surface of the movable base plate, and the recess is closed by a fixed wall on the back surface side provided in the housing, thus defining a back pressure chamber. The compression chamber during volume-reducing process is in communication with the back pressure chamber through a supply passage. High-pressure refrigerant gas is introduced from the compression chamber into the back pressure chamber through the supply passage. In the movable scroll member, a check valve is arranged in the supply passage for blocking the refrigerant gas from back-flowing from the back pressure chamber to the compression chamber.

[0005] Accordingly, the pressure in the back pressure chamber applies back pressure force, which opposes thrust force based upon the pressure in the compression chamber, to the movable scroll member. Thus, sliding resistance is reduced between the movable base plate of the movable scroll member and the fixed wall on the back surface side, on which the back surface of the movable base plate slides.

[0006] The pressure in the back pressure chamber, that is, the back pressure force applied to the movable scroll member, is appropriately adjusted so that the clearance (passing cross-sectional area of the refrigerant gas) between the movable base plate of the movable scroll member and the fixed wall on the back surface side varies. In other words, for example, as the pressure in the compression chamber rises, the thrust force applied to the movable scroll member increases, with the result of the minimum (zero) clearance between the movable base plate and the fixed wall on the back surface side. Accordingly, the refrigerant gas is blocked from being bled from the back pressure chamber to the suction pressure region through the clearance, and the pressure in the back pressure chamber, that is, the back pressure force applied to the movable scroll member tends to increase.

[0007] On the contrary, as the pressure in the compression chamber falls, the thrust force applied to the movable scroll member decreases, with the result of the increased clearance between the movable base plate and the fixed wall on the back surface side. Accordingly, the amount of refrigerant gas bled from the back pressure chamber to the suction pressure region through the clearance increases, and the pressure in the back pressure chamber, that is, the back pressure force applied to the movable scroll member tends to decrease.

[0008] Then, the valve-opening operation of the check valve bleeds the refrigerant gas in the back pressure chamber to the suction pressure region before the high-pressure refrigerant gas in the compression chamber is bled to the back pressure chamber. Accordingly, the movable scroll member instantaneously contacts the fixed wall on the back surface side with its movable base plate by the thrust force, so that the high-pressure refrigerant gas in the compression chamber, that is, the refrigerant gas that has finished its compression work is prevented from uselessly flowing out to the suction pressure region through the supply passage and the back pressure chamber. This leads to improved efficiency of the scroll type compressor.

[0009] In the JP-A-2000-249086, in addition to the clearance (a portion that functions as a valve) between the movable base plate and the fixed wall on the back surface side, the check valve needs to be arranged in the supply passage in the movable scroll member, therefore, there has particularly been a problem that it needs much effort to assemble the check valve to the movable scroll member. That is, in the JP-A-2000-249086 with the complicated valve structure for adjusting the back pressure, there has been a problem that it needs much cost and work for manufacturing a scroll type compressor. Therefore, there is a need for providing a scroll type compressor that has a simple valve structure for adjusting back pressure force.

[0010] US-A-5 989 000 discloses a generic scroll type compressor, which comprises a housing defining a discharge pressure region, a fixed scroll member having a fixed base plate and a fixed scroll wall extending from a surface of the fixed base plate, a movable scroll member having a movable base plate and a movable scroll wall extending from a surface of the movable base plate, wherein the movable scroll wall being engaged with the fixed scroll wall, the fixed scroll member and the movable scroll member being arranged in the housing and defining therebetween a compression chamber, which moves radially and inwardly to progressively reduce the volume of the compression chamber for compressing gas by orbital motion of the movable scroll member. A first fixed wall is provided in the housing for slidably supporting a surface of the movable scroll member. A back pressure chamber is defined on a back surface side of the movable base plate in the housing. A supply passage connects the back pressure chamber to the discharge pressure region and passes through a sliding portion between the movable scroll member and the first fixed wall. Further, a clearance at the sliding portion varies in response to a position of the movable scroll member in a direction in which the movable scroll member approaches to or leaves from the first fixed wall, whereby cross-sectional area of the clearance where the gas passes is varied to adjust pressure in the back pressure chamber.

[0011] JP-A-05-001677 discloses a scroll type compressor that adjusts a back pressure of a back pressure chamber by a complex piston arrangement functioning as a check valve within a movable scroll member of the compressor.

SUMMARY OF THE INVENTION

[0012] It is an object of the present invention to further develop a scroll type compressor according to the preamble of claim 1 such that a valve structure of the invention for adjusting back pressure force is simplified.

[0013] This object is achieved by a scroll type compressor having the features of claim 1.

[0014] Further advantageous developments are defined in the dependent claims.

[0015] It is an advantage of the present invention that costs and processes for manufacturing the scroll type compressor are reduced.

[0016] In accordance with the present invention, a scroll type compressor comprising a housing, a fixed scroll member, a movable scroll member, a first fixed wall, a back pressure chamber, and a supply passage. The housing defines a discharge pressure region. The fixed scroll member has a fixed base plate and a fixed scroll wall extending from a surface of the fixed base plate. The movable scroll member has a movable base plate and a movable scroll wall extending from a surface of the movable base plate. The movable scroll wall is engaged with the fixed scroll wall. The fixed scroll member and the movable scroll member are arranged in the housing and define therebetween a compression chamber, which moves radially and inwardly to progressively reduce the volume of the compression chamber for compressing gas by orbital motion of the movable scroll member. The first fixed wall is provided in the housing radially outside the fixed scroll wall for slidably supporting a surface of the movable scroll member. The back pressure chamber is defined on a back surface side of the movable base plate in the housing. The supply passage connects the back pressure chamber to the discharge pressure region and passes through a sliding portion between the movable scroll member and the first fixed wall, wherein a clearance at the sliding portion varies in response to a position of the movable scroll member in a direction in which the movable scroll member approaches to or leaves from the first fixed wall, whereby cross-sectional area of the clearance where the gas passes is varied to adjust pressure in the back pressure chamber.

[0017] Other aspects and advantages of the invention will become apparent from the following description, taken in conjunction with the accompanying drawings, illustrating by way of example the principles of the invention.

BRIEF DESCRIPTION OF THE DRAWINGS

[0018] The invention together with the object and advantages thereof, may best be understood by reference to the following description of the presently preferred embodiments together with the accompanying drawings in which:

FIG. 1 is a longitudinal cross-sectional view of a motor compressor according to a preferred embodiment of the present invention;

FIG. 2 is a partially enlarged cross-sectional view of FIG. 1; and

FIG. 3 is a back view of a movable scroll member according to the preferred embodiment of the present invention.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0019] A preferred embodiment in which a scroll type compressor according to the present invention is applied to a motor compressor for use in a refrigerant circuit of a vehicle air conditioner will now be described. It is noted that refrigerant for the refrigerant circuit employs carbon dioxide.

[0020] As shown in FIG. 1, the motor compressor has a housing 11, which is made by fixedly connecting a first housing component 12 with a second housing component 13. The first housing component 12 has a cylindrical shape that has a bottom on the left side in FIG. 1. The second housing component 13 has a cylindrical shape that has a bottom on the right side in FIG. 1.

[0021] The first housing component 12 has a cylindrical shaft support portion 12a, which is integrally formed on the bottom center of the inner wall surface of the first housing component 12. The first housing component 12 fixedly accommodates a shaft support member 14 at the opening end thereof. The shaft support member 14 includes a cylindrical portion 15 at the center, which forms therein a hole 15a, and a flange-like disc-shaped portion or a second fixed wall 16, which is formed at the right end of the cylindrical portion 15 in FIG. 1.

[0022] The first housing component 12 accommodates a rotary shaft 18. The rotary shaft 18 is rotatably supported at its left end by a bearing 19, which is placed in the shaft support portion 12a, and is accommodated and rotatably supported at its right end in the hole 15a of the cylindrical portion 15 of the shaft support member 14 by a bearing 20.

[0023] The housing 11 forms therein a motor chamber 22 in a region at the left side in FIG. 1 with respect to the shaft support member 14. In the motor chamber 22, a stator 25 is fixed to the inner cylindrical surface of the first housing component 12, and a rotor 26 is secured to the rotary shaft 18 and located radially inside the stator 25. The stator 25 and the rotor 26 cooperate to form an electric motor. Accordingly, as the stator 25 is externally supplied with electric current, the rotor 26 and the rotary shaft 18 are integrally rotated.

[0024] A fixed scroll member 31 is accommodated in the first housing component 12 and located on the right side with respect to the shaft support member 14 in FIG. 1. The fixed scroll member 31 has a disc-shaped fixed base plate 32. A cylindrical outer peripheral wall 33 extends from the outermost peripheral portion of a front surface 32a of the fixed base plate 32. A fixed scroll wall 34 extends from the radially inner portion of the front surface 32a of the fixed base plate 32 with respect to the outer peripheral wall 33. A tip seal 35 is provided on the distal end surface of the fixed scroll wall 34. The fixed scroll member 31 is fixedly connected at the end surface of the outer peripheral wall 33 to the outermost peripheral portion of the disc-shaped portion 16 of the shaft support member 14.

[0025] A crankshaft 36 is formed on the right end surface of the rotary shaft 18 and accommodated in the right side of the shaft support member 14 and is offset from the axis L of the rotary shaft 18. A bushing 37 is fixedly fitted around the crankshaft 36. A bearing 49 is supported on the bushing 37. A movable scroll member 38 is supported on the bearing 49. A balancer 37a is provided on one end of the bushing 37 on the side of the bearing 20. The balancer 37a reduces rotational imbalance of the rotary shaft 18 due to the offset arrangement of the movable scroll member 38 around the axis L.

[0026] The movable scroll member 38 has a disc-shaped movable base plate 40 and a movable scroll wall 41 that extends from a front surface 40a of the movable base plate 40 toward the fixed base plate 32. A tip seal 44 is provided on the distal end surface of the movable scroll wall 41. The movable scroll member 38 has a boss 43 that extends from the center of a back surface 40b of the movable base plate 40. The boss 43 is fitted around the bearing 49 on the bushing 37. The movable base plate 40 slidably contacts the back surface 16a of the disc-shaped portion 16 (or a second fixed wall) of the shaft support member 14 at its outer peripheral portion of the back surface 40b.

[0027] The fixed scroll member 31 and the movable scroll member 38 are engaged with each other by their scroll walls 34, 41, and slidably contact at their end surfaces of the scroll walls 34, 41 with the base plates 40, 32 of the opposing scroll members 38, 31, respectively. Accordingly, The fixed scroll member 31 and the movable scroll member 38 define therebetween compression chambers 47 by their base plates 32, 40 and scroll walls 34, 41. Incidentally, in the movable and fixed scroll members 38, 31, "front" is the facing side of the compression chambers 47 and "back" is the opposite side of the compression chambers 47.

[0028] A plurality of self-rotation blocking mechanisms 48 (only one of them shown in FIG. 1) are provided between the front surface 40a of the movable base plate 40 of the movable scroll member 38 and the front surface 32a of the fixed base plate 32 of the fixed scroll member 31. Each of the self-rotation blocking mechanisms 48 includes a pair of pins 48a, 48b, and a ring 48c. One pin 48a is fixed to the outermost peripheral portion of the front surface 40a in the movable base plate 40. The other pin 48b is fixed to the outer peripheral portion (which is inside the outer peripheral wall 32) of the front surface 32a of the fixed base plate 32. The ring 48c is located outside the pins 48a, 48b to prevent the pins 48a, 48b from being radially spaced away from each other.

[0029] The outer peripheral wall 33 of the fixed scroll member 31 and the outermost peripheral portion of the movable scroll wall 41 of the movable scroll member 38 define therebetween a suction chamber 51. The outer peripheral portion of the disc-shaped portion 16 of the shaft support member 14 forms therein a suction port 39 that connects the suction chamber 51 to the motor chamber 22. The first housing component 12 forms therein an inlet 50 that communicates with the motor chamber 22. An external conduit that connects with the outlet of an evaporator of an external refrigerant circuit (not shown) is connected to the inlet 50. Accordingly, low-pressure refrigerant gas from the external refrigerant circuit is introduced into the suction chamber 51 through the inlet 50, the motor chamber 22, and the suction port 39.

[0030] The second housing component 13 and the fixed scroll member 31 define therebetween a discharge chamber 52 in the housing 11. The fixed scroll member 31 forms a discharge port 31 a at the center of the fixed base plate 32 thereof. In the discharge chamber 52, a discharge valve 58 made of a flapper valve is attached to the back surface 32b of the fixed base plate 32 of the fixed scroll member 31. The innermost compression chamber 47 communicates with the discharge chamber 52 through the discharge port 31 a. The second housing component 13 forms therein an outlet 53 that communicates with the discharge chamber 52.

[0031] In the discharge chamber 52, a separation pipe 68 is attached to the opening of the outlet 53. The separation pipe 68, for example, prevents lubricating oil (refrigerating machine oil) in the discharge chamber 52 from flowing to the outlet 53 along the inner wall surface of the discharge chamber 52, thus functioning as a kind of oil separator. An external conduit, which connects with the inlet of a gas cooler of the external refrigerant circuit (not shown), is connected to the outlet 53 outside the second housing component 13. Accordingly, the refrigerant gas in the discharge chamber 52 is bled to the external refrigerant circuit through the separation pipe 68 and the outlet 53.

[0032] As the rotary shaft 18 is rotated, the movable scroll member 38 is orbited around the axis (the axis L of the rotary shaft 18) of the fixed scroll member 31 through the crankshaft 36. At the same time, the self-rotation blocking mechanism 48 blocks the self-rotating motion of the movable scroll member 38, and only the orbital motion thereof is permitted. By the orbital motion of the movable scroll member 38, the compression chambers 47 progressively reduce their volumes as they move radially and inwardly from the outer peripheral side of the scroll walls 34, 41 of the scroll members 31, 38 toward the center thereof, thus compressing the low-pressure refrigerant gas, which is introduced into the compression chamber 47 from the suction chamber 51. The high-pressure refrigerant gas, which has been compressed, is discharged from the innermost compression chamber 47 to the discharge chamber 52 through the discharge port 31 a by pushing away the discharge valve 58.

[0033] The adjustment function for the back pressure force applied to the movable scroll member 38 will now be described.

[0034] As shown in FIGS. 2 and 3, in the movable base plate 40 of the movable scroll member 38, an annular recess 55 is recessed on the outer peripheral portion of the back surface 40b in the annular region along the outline circle of the movable base plate 40. The annular recess 55 is closed by the back surface 16a of the disc-shaped portion 16 of the shaft support member 14. Accordingly, the back surface 40b of the movable base plate 40 and the back surface 16a of the disc-shaped portion 16 of the shaft support member 14, which form therebetween an inner space of the annular recess 55 that is closed by the disc-shaped portion 16, define a back pressure chamber 56.

[0035] As shown in FIG. 2, in the shaft support member 14, an inner tip seal 66 is provided radially inward with respect to the back pressure chamber 56 on the back surface 16a of the disc-shaped portion 16. In the movable scroll member 38, an outer tip seal 67 is provided radially outward with respect to the back pressure chamber 56 on the back surface 40b of the movable base plate 40. The inner tip seal 66 slidably contacts the back surface 40b of the movable base plate 40, and the outer tip seal 67 slidably contacts the back surface 16a of the disc-shaped portion 16 of the shaft support member 14, so that the back pressure chamber 56 is sealed from the ambient atmosphere.

[0036] The shaft support member 14 forms therein a bleed passage 57 that coordinates with the back pressure chamber 56. The bleed passage 57 opens at its one end (an opening 57a) at the back surface 16a of the disc-shaped portion 16 of the shaft support member 14 to communicate with the back pressure chamber 56, and opens at its other end (an opening 57b) into the hole 15a of the cylindrical portion 15 of the shaft support member 14. The hole 15a of the cylindrical portion 15 communicates with the motor chamber 22 (shown in FIG. 1) to have the same atmospheric pressure as the motor chamber 22, that is, the hole 15a is a part of a suction pressure region. In the bleed passage 57, a fixed throttle 57c is provided between the opening 57b and the hole 15a.

[0037] In the movable scroll member 38, a movable passage 59 is formed around the lowermost portion of the movable base plate 40 to coordinate with the back pressure chamber 56. The movable passage 59 opens at its one end (an opening 59a) into the back pressure chamber 56, and opens at its other end (an opening 59b) at the front surface 40a of the movable base plate 40. In the fixed scroll member 31, a fixed passage 60 is formed around the lowermost portion of the fixed base plate 32 to coordinate with the movable passage 59.

[0038] In the fixed base plate 32 of the fixed scroll member 31, a first fixed wall 69, which is formed to face the front surface 40a of the movable base plate 40, is located radially inside the outer peripheral wall 33 and radially outside the fixed scroll wall 34 around the lowermost portion of the fixed base plate 32. That is, the first fixed wall 69 is provided at a portion of the front surface 32a of the fixed base plate 32 that is different from the fixed scroll wall 34. An end surface 69a of the first fixed wall 69 and the front surface 40a of the movable base plate 40 slidably contact each other (a sliding portion between the movable scroll member 38 and the first fixed wall 69).

[0039] The fixed passage 60 extends through the first fixed wall 69 from the fixed base plate 32 toward the movable base plate 40. The fixed passage 60 opens at its one end (an opening 60a) on the end surface 69a of the first fixed wall 69, and opens at its other end (an opening 60b) around the lowermost portion of the back surface 32b of the fixed base plate 32, that is, around the lowermost portion in the discharge chamber 52.

[0040] The lubricating oil, which is separated from the refrigerant gas by the separation pipe 68, drops to be reserved around the lowermost portion of the discharge chamber 52. That is, the region around the lowermost portion in the discharge chamber 52 is regarded as a reservoir space 52a for reserving the lubricating oil that is separated by the separation pipe 68. In the reservoir space 52a, a filter 61 is provided at the opening 60b of the fixed passage 60 on the back surface 32b of the fixed base plate 32 of the fixed scroll member 31. The filter 61 is to remove foreign substances from the lubricating oil that flows from the reservoir space 52a to the fixed passage 60.

[0041] On the end surface 69a of the first fixed wall 69 of the fixed scroll member 31, a communication recess 62 is formed around the opening 60a of the fixed passage 60. The communication recess 62 has an annular shape that extends along a locus that the opening 59b of the movable passage 59 tracks by the orbital motion of the movable scroll member 38. Accordingly, the opening 59b of the movable passage 59 constantly faces the communication recess 62 even if the movable scroll member 38 is located at any orbital position. The fixed passage 60, the communication recess 62 and the movable passage 59 cooperate to form a supply passage that connects the discharge chamber or a discharge pressure region 52 (the reservoir space 52a) to the back pressure chamber 56.

[0042] On the end surface 69a of the first fixed wall 69 of the fixed scroll member 31, a tip seal 63 is placed around the communication recess 62 to slidably contact the front surface 40a of the movable base plate 40 of the movable scroll member 38. The communication recess 62 and the opening 59b of the movable passage 59 are in communication with each other inside the tip seal 63, that is, in a state where they are sealed by the tip seal 63 from the ambient atmosphere. This leads to prevented leakage of high-pressure refrigerant gas from the supply passage, that is, prevented decrease in efficiency of the motor compressor.

[0043] On the end surface 69a of the first fixed wall 69 of the fixed scroll member 31, a region around the opening 60a of the fixed passage 60 and surrounded by the communication recess 62 functions as a valve seat 64. On the end surface 69a of the first fixed wall 69, a region around the opening 59b of the movable passage 59 and facing the valve seat 64 functions as a valve portion 65.

[0044] As the movable scroll member 38 (the movable base plate 40) moves away from the fixed scroll member 31 (the first fixed wall 69) with respect to the direction along the axis L of the rotary shaft 18, the valve portion 65 leaves from the valve seat 64 to increase the clearance therebetween. On the contrary, as the movable scroll member 38 moves to approach the fixed scroll member 31, the valve portion 65 approaches the valve seat 64 to reduce the clearance therebetween.

[0045] As the pressure in the discharge chamber 52 rises by starting the operation of the motor compressor, the high-pressure refrigerant gas in the discharge chamber 52 is introduced into the back pressure chamber 56 through the fixed passage 60, the communication recess 62, and the movable passage 59. The refrigerant gas in the back pressure chamber 56 is bled to the motor chamber 22 through the bleed passage 57 and the hole 15a. The pressure in the back pressure chamber 56 is determined based upon the balance between the amount of high-pressure refrigerant gas from the discharge chamber 52 into the back pressure chamber 56 and the amount of refrigerant gas bled through the bleed passage 57.

[0046] The back pressure force is applied to the movable scroll member 38 based upon the pressure in the back pressure chamber 56 to urge the movable scroll member 38 toward the fixed scroll member 31 in the direction along the axis L. The thrust force is applied to the movable scroll member 38 based upon the pressure in the compression chamber 47 in the direction away from the fixed scroll member 31 along the axis L. Thus, in response to the balance between the back pressure force and the thrust force, a position of the movable scroll member 38 relative to the fixed scroll member 31 in the direction along the axis L is determined.

[0047] For example, as the pressure in the compression chamber 47 reduces to let the thrust force be below the back pressure force, the back surface 40b of the movable base plate 40 of the movable scroll member 38 is moved by the back pressure force away from the back surface 16a of the disc-shaped portion 16 of the shaft support member 14. The movable base plate 40 of the movable scroll member 38 leaves away from the disc-shaped portion 16, and the front surface 40a of the movable base plate 40 contacts with the end surface 69a of the first fixed wall 69 of the fixed scroll member 31, thus the clearance between the valve seat 64 and the valve portion 65 becomes minimum (zero).

[0048] As the clearance between the valve seat 64 and the valve portion 65 becomes minimum, the passing cross-sectional area of refrigerant gas between the fixed passage 60 and the communication recess 62, that is, the opening degree of the supply passage, becomes minimum (zero). Accordingly, the high-pressure refrigerant gas is prevented from being introduced from the discharge chamber 52 to the back pressure chamber 56 through the fixed passage 60, the communication recess 62, and the movable passage 59. Then, the pressure in the back pressure chamber 56 tends to fall, and the back pressure force applied to the movable scroll member 38 reduces.

[0049] For reducing the back pressure force applied to the movable scroll member 38, the clearance between the valve seat 64 and the valve portion 65 becomes minimum to prevent the high-pressure refrigerant gas from being introduced from the discharge chamber 52 to the back pressure chamber 56. Accordingly, the high-pressure refrigerant gas in the discharge chamber 52, that is, the compressed refrigerant gas, is prevented from uselessly flowing .to the motor chamber 22 through the supply passage, the back pressure chamber 56 and the bleed passage 57. This leads to improved performance of the motor compressor.

[0050] As the thrust force exceeds the back pressure force due to increase in pressure in the compression chamber 47, the movable scroll member 38 is moved by the thrust force in the direction in which the back surface 40b of the movable base plate 40 approaches the back surface 16a of the disc-shaped portion 16 of the shaft support member 14. As the front surface 40a of the movable base plate 40 leaves away from the end surface 69a of the first fixed wall 69 of the fixed scroll member 31 so that the movable base plate 40 of the movable scroll member 38 contacts the disc-shaped portion 16 of the shaft support member 14, the clearance between the valve seat 64 and the valve portion 65 becomes maximum.

[0051] As the clearance between the valve seat 64 and the valve portion 65 becomes maximum, the passing cross-sectional area of the refrigerant gas between the fixed passage 60 and the communication recess 62, that is, the opening degree of the supply passage becomes maximum. Accordingly, the high-pressure refrigerant gas is introduced from the discharge chamber 52 to the back pressure chamber 56 through the fixed passage 60, the communication recess 62 and the movable passage 59. Thus, the pressure in the back pressure chamber tends to increase, and the back pressure force applied to the movable scroll member 38 increases.

[0052] At the same time, the refrigerant gas is slowly bled from the back pressure chamber 56 to the motor chamber 22 through the bleed passage 57 due to the fixed throttle 57c in the bleed passage 57. Accordingly, the high-pressure refrigerant gas in the discharge chamber 52, that is, the compressed refrigerant gas is prevented from uselessly flowing to the motor chamber 22 through the supply passage, the back pressure chamber 56 and the bleed passage 57. This leads to improved performance of the motor compressor.

[0053] As described above, the movable scroll member 38 varies the clearance between the front surface 40a of the movable base plate 40 and the end surface 69a of the first fixed wall 69 of the fixed scroll member 31 (the clearance between the valve seat 64 and the valve portion 65) so that the back pressure force based upon the pressure in the back pressure chamber 56 becomes an appropriate value in response to the thrust force based upon the pressure in the compression chambers 47, thus autonomously adjusting the pressure in the back pressure chamber 56. As the pressure in the back pressure chamber 56 is appropriately adjusted, generation of sliding resistance due to the orbital motion of the movable scroll member 38 is reduced.

[0054] According to the preferred embodiment, the following advantageous effects are obtained.

(1) To adjust the pressure in the back pressure chamber 56, that is, to adjust the back pressure force applied to the movable scroll member 38, the opening degree of the supply passage (the fixed passage 60, the movable passage 59, and the communication recess 62) is adjusted by varying the clearance at the sliding portion between the movable scroll member 38 and the first fixed wall 69. Accordingly, to decrease the back pressure force applied to the movable scroll member 38, the introduction of the high-pressure refrigerant gas from the discharge chamber 52 to the back pressure chamber 56 is prevented by minimizing clearance at the sliding portion between the movable scroll member 38 and the first fixed wall 69. Thus, for example, the check valve disclosed in Unexamined Japanese Patent Publication No. 2000-249086 is not required for closing the supply passage, so that the valve structure for adjusting the back pressure force is simple, and costs and processes are reduced for manufacturing the motor compressor.

(2) In the preferred embodiment, the front surface 40a of the movable base plate 40 is the front surface of the movable scroll member according to the present invention, and the first fixed wall 69 is provided on the front surface 32a of the fixed base plate 32 at a position that is different from the fixed scroll wall 34. That is, the first fixed wall 69 is provided in the fixed scroll member 31 exclusively for the supply passage and independently from the fixed base plate 32 and the fixed scroll wall 34. Accordingly, in comparison to employment of the radially thin fixed scroll wall 34 as a first fixed wall, or in comparison to employment of the region that slides on the movable scroll wall 41 in the fixed base plate 32 as a first fixed wall, the supply passage easily passes through the sliding portion between the movable scroll member 38 and the first fixed wall 69, that is, the arrangement of the supply passage (especially, the formation of the valve seat 64 and the valve portion 65) becomes easy.

(3) The back pressure chamber 56 is defined between the movable base plate 40 and the disc-shaped portion 16 of the shaft support member 14. The self-rotation blocking mechanism 48 is provided between the movable base plate 40 and the fixed base plate 32. In other words, the arrangement of the self-rotation blocking mechanism 48 between the movable base plate 40 and the fixed base plate 32 prevents a complicated space on the side of the back surface 40b of the movable base plate 40. Accordingly, the back pressure chamber 56 defined between the movable base plate 40 and the disc-shaped portion 16 of the shaft support member 14 becomes relatively free in arrangement and formation. Thus, in the preferred embodiment, the annular back pressure chamber 56 (the annular recess 55) is arranged along the outline of the movable base plate 40 at the outer peripheral portion of the back surface 40b of the movable base plate 40.

(4) Lubricating oil is introduced together with the high-pressure refrigerant gas from the region around the lowermost portion of the discharge chamber 52, that is, the reservoir space 52 for lubricating oil to the back pressure chamber 56. Accordingly, a sufficient amount of lubricating oil is supplied to, for example, the sliding portion between the movable base plate 40 of the movable scroll member 38 and the disc-shaped portion 16 of the shaft support member 14, and the sliding portion between the movable base plate 40 and the first fixed wall 69 of the fixed scroll member 31, thus appropriately lubricating the sliding portions.

(5) The filter 61 is placed at the opening 60b of the fixed passage 60 in the reservoir space 52a. Accordingly, foreign substances in the reservoir space 52a are prevented from being introduced into the fixed passage 60, and also prevented from being introduced, for example, into the sliding portion between the movable base plate 40 and the first fixed wall 69 of the fixed scroll member 31, the sliding portion between the movable base plate 40 and the disc-shaped portion 16 of the shaft support member 14, or the like. Thus, the front surface 40a and the back surface 40b of the movable base plate 40, the end surface 69a of the first fixed wall 69, the back surface 16a of the disc-shaped portion 16 and the like are prevented from being damaged by foreign substances.

(6) Carbon dioxide is employed as refrigerant for the refrigerant circuit. The present invention is particularly efficient in carbon dioxide refrigerant in which large thrust force is applied to the movable scroll member 38.

[0055] The present invention is not limited to the embodiments described above but may be modified into the following alternative embodiments.

[0056] In an alternative embodiment to the above preferred embodiment, the bleed passage 57 is omitted. In this case, a decrease in the pressure in the back pressure chamber 56 is achieved by the leakage of refrigerant gas from the inner tip seal 66 or the outer tip seal 67. Alternatively, one of the inner tip seal 66 and the outer tip seal 67 is omitted, and refrigerant gas in the back pressure chamber 56 is leaked through the clearance at the sliding portion between the back surface 40b of the movable base plate 40 and the back surface 16a of the disc-shaped portion 16 of the shaft support member 14. Furthermore, in at least one of the inner tip seal 69 and the outer tip seal 67, sealing performance is partially decreased by forming a notch, and refrigerant gas is leaked from the back pressure chamber 56 through the portion that is decreased in sealing performance. Anyway, a path through which refrigerant gas is bled from the back pressure chamber 56 may be regarded as a bleed passage.

[0057] In the preferred embodiment, the high-pressure refrigerant gas is introduced from the discharge chamber 52 into the back pressure chamber 56 through the reservoir space 52a. In an alternative embodiment, the high-pressure refrigerant gas is introduced from the upper side of the discharge chamber 52 (the region other than the reservoir space 52a) to the back pressure chamber 56, or is introduced from the discharge port 31 a to the back pressure chamber 56, or is introduced from the compression chamber 47 that is in a discharge process (the compression chamber 47 that is in communication with the discharge port 31 a) to the back pressure chamber 56. Additionally, the high-pressure refrigerant gas is introduced from an external conduit that communicates with, for example, the outlet 53, to the back pressure chamber 56.

[0058] In the preferred embodiment, the first fixed wall 69 is exclusively provided for the supply passage in the fixed scroll member 31 and independently from the fixed base plate 32 and the fixed scroll wall 34. However, the structure is not limited. In an alternative embodiment, the first fixed wall 69 is omitted, and the fixed base plate 32 doubles as the first fixed wall (the former), or the fixed scroll wall 34 doubles as the first fixed wall (the latter). Thus, in comparison to the structure that the first fixed wall is provided exclusively for the supply passage, the structure of the fixed scroll member 31 is simplified.

[0059] In the former case, the supply passage passes through the sliding portion between the front surface 32a of the fixed base plate 32 of the fixed scroll member 31 and, for example, the distal end surface of the movable scroll wall 41 of the movable scroll member 38. Also, in the latter case, the supply passage passes through the sliding portion between the distal end surface of the fixed scroll wall 34 of the fixed scroll member 31 and the front surface 40a of the movable base plate 40 of the movable scroll member 38.

[0060] It is noted that in the former case, a wall (a wall other than the movable scroll wall 41) is provided exclusively for the supply passage on the front surface 40a of the movable base plate 40, and the supply passage passes through the sliding portion between the end surface of the wall and the front surface 32a of the fixed base plate 32.

[0061] In the preferred embodiment, the first fixed wall 69 is provided for the fixed scroll member 31. However, it is not limited. In an alternative embodiment, for example, a member corresponding to the first fixed wall 69 is provided independently from the fixed scroll member 31.

[0062] In an alternative embodiment to the preferred embodiment, the hole 15a is isolated from the motor chamber 22 to use the isolated space as the back pressure chamber by placing a seal member in the boss 15 of the shaft support member 14 for sealing the rotary shaft 18. In this case, the portion corresponding to the bleed passage 57 and the back pressure chamber 56 is regarded as a part of the supply passage by omitting the fixed throttle 57c from the bleed passage 57 in the preferred embodiment. Also, in this case, a bleed passage having a fixed throttle may, for example, be provided for the shaft support member 14 so as to connect the above isolated space to the suction pressure region (for example, the motor chamber 22 or the suction chamber 51). .

[0063] In an alternative embodiment to the preferred embodiment, the suction port 39 is omitted, while the inlet 50 directly opens to the suction chamber 51. Then, the hole 15a of the boss 15 of the shaft support member 14 is used as a back pressure chamber. Accordingly, the motor chamber 22 that communicates with the hole 15a is an atmosphere of the pressure in the back pressure chamber. In this case, the portion corresponding to the bleed passage 57 and the back pressure chamber 56 is regarded as a part of the supply passage by omitting the fixed throttle 57c from the bleed passage 57 in the preferred embodiment. Also, in this case, for example, a bleed passage having a fixed throttle may be provided for the shaft support member 14 so as to connect the motor chamber 22 to the suction pressure region (for example, the suction chamber 51).

[0064] In the preferred embodiment, the self-rotation blocking mechanism 48 includes the pin 48a fixed to the movable base plate 40, the pin 48b fixed to the fixed base plate 32, and the ring 48c arranged outside the pins 48a, 48b. However, it is not limited. In an alternative embodiment, a pin is fixed to the front surface 40a of the movable base plate 40, while a circular recess for guiding the orbital motion of the pin is formed in the front surface 32a of the fixed base plate 32.

[0065] In the preferred embodiment, the self-rotation blocking mechanisms 48 are provided between the movable base plate 40 and the fixed base plate 32. In an alternative embodiment, the self-rotation blocking mechanisms 48 are provided between the movable base plate 40 and the disc-shaped portion 16 of the shaft support member 14. In this case, the back pressure chamber 56 is formed to avoid the self-rotation blocking mechanism 48.

[0066] The present invention is not limited to a motor compressor, that is, a scroll type compressor that only employs an electric motor as a drive source, but may be a scroll type compressor that employs a vehicular engine as a drive source or a hybrid scroll type compressor that employs an electric motor and an engine as a drive source.

[0067] The present invention may be applied to a scroll type compressor for a refrigerant circuit employing fluorocarbon refrigerant.

[0068] The present invention may be applied to, for example, an air compressor used for other than a refrigerant circuit.

[0069] Therefore, the present examples and embodiments are to be considered as illustrative and not restrictive, and the invention is not to be limited to the details given herein but may be modified within the scope of the appended claims.

Claims

1. A scroll type compressor comprising

a housing (11) defining a discharge pressure region (52),

a fixed scroll member (31) having a fixed base plate (32) and a fixed scroll wall (34) extending from a surface of the fixed base plate (32),

a movable scroll member (38) having a movable base plate (40) and a movable scroll wall (41) extending from a surface of the movable base plate (40), wherein the movable scroll wall (41) being engaged with the fixed scroll wall (34), the fixed scroll member (31) and the movable scroll member (38) being arranged in the housing (11) and defining therebetween a compression chamber (47), which moves radially and inwardly to progressively reduce the volume of the compression chamber (47) for compressing gas by orbital motion of the movable scroll member (38),

a first fixed wall (69) is provided in the housing (11) for slidably supporting a surface of the movable scroll member (38),

a back pressure chamber (56) is defined on a back surface side of the movable base plate (40) in the housing (11),

a supply passage (59, 60) connects the back pressure chamber (56) to the discharge pressure region (52) and passes through a sliding portion between the movable scroll member (38) and the first fixed wall (69), and

a clearance at the sliding portion varies in response to a position of the movable scroll member (38) in a direction in which the movable scroll member (38) approaches to or leaves from the first fixed wall (69), whereby cross-sectional area of the clearance where the gas passes is varied to adjust pressure in the back pressure chamber (56),

characterized in that
the first fixed wall (69) is located radially outside the fixed scroll wall (34).

2. The scroll type compressor according to claim 1, wherein the surface of the movable scroll member (38) is a front surface (40a) of the movable base plate (40), and the first fixed wall (69) is provided on the surface of the fixed base plate (32) and is located at a position that is different from the fixed scroll wall (34).

3. The scroll type compressor according to any one of claims 1 and 2, characterized in that a second fixed wall (16) is provided in the housing (11) for slidably supporting a back surface (40b) of the movable base plate (40), in that the movable base plate (40) and the second fixed wall (16) define therebetween the back pressure chamber (56).

4. The scroll type compressor according to claim 3, characterized in that a self-rotation blocking mechanism (48) is provided between the movable base plate (40) and the fixed base plate (32) for blocking self-rotation of the movable scroll member (38), while allowing orbital motion of the movable scroll member (38).

5. The scroll type compressor according to any one of claims 1 through 4, characterized in that an oil separator (68) is provided in the housing (11) for separating lubricating oil from the gas discharged from the compression chamber (47), in that a reservoir space (52a) is provided in the housing (11) for reserving the lubricating oil separated by the oil separator (68), and in that the reservoir space (52a) is a part of the discharge pressure region (52) and is in communication with the back pressure chamber (56) through the supply passage (59, 60).

6. The scroll type compressor according to claim 5, characterized in that a filter (61) is placed at an opening (60b) of the supply passage (59, 60) in the reservoir space (52a).

7. The scroll type compressor according to any one of claims 5 and 6, wherein the lubricating oil is introduced together with high-pressure refrigerant gas from a region around a lowermost portion of the discharge pressure region (52) to the back pressure chamber (56).

8. The scroll type compressor according to any one of claims 1 through 7, wherein the gas is refrigerant for a refrigerant circuit, carbon dioxide being employed as the refrigerant.

9. The scroll type compressor according to any one of claims 1 through 8, wherein the scroll type compressor is driven by an electric motor (25, 26).

10. The scroll type compressor according to any one of claims 1 through 9, wherein the first fixed wall (34) is integrally formed with the fixed scroll member (31).

11. The scroll type compressor according to any one of claims 1 through 10, wherein the supply passage (59, 60) includes a fixed passage (60), a communication recess (62) and a movable passage (59), the communication recess (62) and a region of an opening (60a) of the movable passage (59) respectively functioning as a valve seat (64) and a valve portion (65) to open and close the supply passage (59, 60).

12. The scroll type compressor according to claim 11, wherein the communication recess (62) and the movable passage (59) are continuously communicated with each other.

13. The scroll type compressor according to any one of claims 1 through 12, wherein the housing (11) further defines a suction pressure region (15, 22, 51), the suction pressure region (15, 22, 51) and the back pressure chamber (56) being communicated with each other through a bleed passage (57), wherein a throttle (57c) is provided between an opening (57b) of the bleed passage (57) and the suction pressure region (12, 22, 51).

Ansprüche

1. Spiralverdichter mit

einem Gehäuse (11), das eine Abgabedruckregion (52) definiert,

einem festen Spiralbauteil (31), das eine feste Grundplatte (32) und eine feste Spiralwand (34) hat, die sich von einer Fläche der festen Grundplatte (32) erstreckt,

einem beweglichen Spiralbauteil (38), das eine bewegliche Grundplatte (40) und eine bewegliche Spiralwand (41) hat, die sich von einer Fläche der beweglichen Grundplatte (40) erstreckt, wobei die bewegliche Spiralwand (41) mit der festen Spiralwand (34) in Eingriff ist, wobei das feste Spiralbauteil (31) und das bewegliche Spiralbauteil (38) in dem Gehäuse (11) angeordnet sind und zwischen ihnen eine Verdichtungskammer (47) definieren, die sich radial und nach innen bewegt, um das Volumen der Verdichtungskammer (47) zum Verdichten von Gas durch eine kreisförmige Bewegung des Spiralverdichters (38) fortschreitend zu reduzieren, wobei

eine erste feste Wand (69) in dem Gehäuse (11) zum gleitenden Stützen einer Fläche des beweglichen Spiralbauteils (38) versehen ist,

eine Hinterdruckkammer (56) an einer Seite einer hinteren Fläche der beweglichen Grundplatte (40) in dem Gehäuse (11) definiert ist,

ein Zufuhrdurchgang (59, 60) die Hinterdruckkammer (56) mit der Abgabedruckregion (52) verbindet und durch einen Gleitabschnitt zwischen dem beweglichen Spiralbauteil (38) und der ersten festen Wand (69) hindurchtritt, und

ein Spalt an dem Gleitabschnitt in Erwiderung auf eine Position des beweglichen Spiralbauteils (38) in einer Richtung variiert, in der sich das bewegliche Spiralbauteil (38) der ersten festen Wand (69) nähert oder sich von dieser entfernt, wodurch eine Querschnittsfläche des Spalts, durch den das Gas tritt, variiert wird, um einen Druck in der Hinterdruckkammer (56) einzustellen,

dadurch gekennzeichnet, dass
die erste feste Wand (69) radial außerhalb der festen Spiralwand (34) angeordnet ist.

2. Spiralverdichter nach Anspruch 1, wobei die Fläche des beweglichen Spiralbauteils (38) eine vordere Fläche (40a) der beweglichen Grundplatte (40) ist, und wobei die erste feste Wand (69) an der Fläche der festen Grundplatte (32) versehen ist und an einer Position angeordnet ist, die von der festen Spiralwand (34) verschieden ist.

3. Spiralverdichter nach einem der Ansprüche 1 und 2, dadurch gekennzeichnet, dass
eine zweite feste Wand (16) in dem Gehäuse (11) zum gleitenden Stützen einer hinteren Fläche (40b) der beweglichen Grundplatte (40) versehen ist, und
die bewegliche Grundplatte (40) und die zweite feste Wand (16) zwischen ihnen die Hinterdruckkammer (56) definieren.

4. Spiralverdichter nach Anspruch 3, dadurch gekennzeichnet, dass ein Selbstdrehungsblockiermechanismus (48) zwischen der beweglichen Grundplatte (40) und der festen Grundplatte (32) zum Blockieren einer Selbstdrehung des beweglichen Spiralbauteils (38) vorgesehen ist, während eine kreisförmige Bewegung des beweglichen Spiralbauteils (38) zugelassen wird.

5. Spiralverdichter nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass
ein Ölabscheider (68) in einem Gehäuse (11) zum Abscheiden von Schmieröl von dem Gas vorgesehen ist, das von der Verdichtungskammer (47) abgegeben wird,
ein Speicherraum (52a) in dem Gehäuse (11) zum Speichern des Schmieröls vorgesehen ist, das durch den Ölabscheider (68) abgeschieden wird, und
der Speicherraum (52a) ein Teil der Abgabedruckregion (52) ist und durch den Zufuhrdurchgang (59, 60) mit der Hinterdruckkammer (56) in Verbindung ist.

6. Spiralverdichter nach Anspruch 5, dadurch gekennzeichnet, dass ein Filter (61) an einer Öffnung (60b) des Zufuhrdurchgangs (59, 60) in dem Speicherraum (52a) angeordnet ist.

7. Spiralverdichter nach einem der Ansprüche 5 und 6, wobei das Schmieröl gemeinsam mit einem Hochdruckkältemittelgas von einer Region um einen untersten Abschnitt der Abgabedruckregion (52) zu der Hinterdruckkammer (56) eingebracht wird.

8. Spiralverdichter nach einem der Ansprüche 1 bis 7, wobei das Gas ein Kältemittel für einen Kältemittelkreislauf ist, wobei Kohlenstoffdioxid als das Kältemittel angewandt wird.

9. Spiralverdichter nach einem der Ansprüche 1 bis 8, wobei der Spiralverdichter durch einen Elektromotor (25, 26) angetrieben wird.

10. Spiralverdichter nach einem der Ansprüche 1 bis 9, wobei die erste feste Wand (34) einstückig mit dem festen Spiralbauteil (31) ausgebildet ist.

11. Spiralverdichter nach einem der Ansprüche 1 bis 10, wobei der Zufuhrdurchgang (59, 60) einen festen Durchgang (60), eine Verbindungsaussparung (62) und einen beweglichen Durchgang (59) hat, wobei die Verbindungsaussparung (62) und eine Region einer Öffnung (60a) des beweglichen Durchgangs (59) als ein Ventilsitz (64) bzw. ein Ventilabschnitt (65) wirken, um den Zufuhrdurchgang (59, 60) zu öffnen und zu schließen.

12. Spiralverdichter nach Anspruch 11, wobei die Verbindungsaussparung (62) und der bewegliche Durchgang (59) miteinander kontinuierlich verbunden sind.

13. Spiralverdichter nach einem der Ansprüche 1 bis 12, wobei das Gehäuse (11) weiter eine Saugdruckregion (15, 22, 51) definiert, wobei die Saugdruckregion (15, 22, 51) und die Hinterdruckkammer (56) miteinander durch einen Ausströmdurchgang (57) verbunden sind, wobei eine Drossel (57c) zwischen einer Öffnung (57b) des Ausströmdurchgangs (57) und der Saugdruckregion (12, 22, 51) vorgesehen ist.

Revendications

1. Compresseur à spirale, comprenant

un carter (11) définissant une zone de pression refoulement (52),

un élément formant spirale fixe (31) ayant une plaque de base fixe (32) et une paroi de spirale fixe (34) s'étendant depuis une surface de la plaque de base fixe (32),

un élément formant spirale mobile (38) ayant une plaque de base mobile (40) et une paroi de spirale mobile (41) s'étendant depuis une surface de la plaque de base mobile (40), dans lequel la paroi de spirale mobile (41) est en prise avec la paroi de spirale fixe (34), l'élément formant spirale fixe (31) et l'élément formant spirale mobile (38) étant disposés dans le carter (11) et définissant entre ceux-ci une chambre de compression (47) qui se déplace radialement et vers l'intérieur pour réduire progressivement le volume de la chambre de compression (47) pour comprimer du gaz par mouvement orbital de l'élément formant spirale mobile (38),

une première paroi fixe (69) positionnée dans le carter (11) pour supporter en coulissement une surface de l'élément formant spirale mobile (38),

une chambre de contre-pression (56) définie sur un côté de surface arrière de la plaque de base mobile (40) dans le carter (11),

un passage d'alimentation (59, 60) reliant la chambre de contre-pression (56) à la zone de pression de refoulement (52) et traversant une partie coulissante entre l'élément formant spirale mobile (38) et la première paroi fixe (69), et

un dégagement au niveau de la partie coulissante variant en réaction à une position de l'élément formant spirale mobile (38) dans un sens dans lequel l'élément formant spirale mobile (38) se rapproche ou s'éloigne de la première paroi fixe (69), moyennant quoi la superficie en coupe du dégagement par lequel le gaz circule est variée pour régler la pression dans la chambre de contre-pression (56),

caractérisé en ce que
la première paroi fixe (69) est positionnée radialement à l'extérieur de la paroi de spirale fixe (34).

2. Compresseur à spirale selon la revendication 1, dans lequel la surface de l'élément formant spirale mobile (38) est une surface avant (40a) de la plaque de base mobile (40), et la première paroi fixe (69) est apportée sur la surface de la plaque de base fixe (32) et elle est positionnée à un emplacement autre de celui de la paroi de spirale fixe (34).

3. Compresseur à spirale selon l'une quelconque des revendications 1 et 2, caractérisé en ce qu'une seconde paroi fixe (16) est apportée dans le carter (11) pour supporter en coulissement une surface arrière (40b) de la plaque de base mobile (40), et en ce que la plaque de base mobile (40) et la seconde paroi fixe (16) définissent entre celles-ci la chambre de contre-pression (56).

4. Compresseur à spirale selon la revendication 3, caractérisé en ce qu'un mécanisme de blocage de rotation automatique (48) est apporté entre la plaque de base mobile (40) et la plaque de base fixe (32) pour bloquer la rotation automatique de l'élément formant spirale mobile (38) tout en permettant le mouvement orbital de l'élément formant spirale fixe (38).

5. Compresseur à spirale selon l'une quelconque des revendications 1 à 4, caractérisé en ce qu'un séparateur d'huile (68) est positionné dans le carter (11) pour séparer l'huile de graissage des gaz refoulés de la chambre de compression (47), en ce qu'un espace formant réservoir (52a) est apporté dans le carter (11) pour réserver l'huile de graissage séparée par le séparateur d'huile (68), et en ce que l'espace formant réservoir (52a) est une partie de la zone de pression de refoulement (52) et il est en communication avec la chambre de contre-pression (56) à travers le passage d'alimentation (59, 60).

6. Compresseur à spirale selon la revendication 5, caractérisé en ce qu'un filtre (61) est positionné à une ouverture (60b) du passage d'alimentation (59, 60) dans l'espace formant réservoir (52a).

7. Compresseur à spirale selon l'une quelconque des revendications 5 et 6, dans lequel l'huile de graissage est introduite en même temps que du gaz frigorigène à haute pression, depuis une zone entourant une partie la plus basse de la zone de pression de refoulement (52) vers la chambre de contre-pression (56).

8. Compresseur à spirale selon l'une quelconque des revendications 1 à 7, dans lequel le gaz est frigorigène pour un circuit de fluide frigorigène, du dioxyde de carbone étant utilisé comme fluide frigorigène.

9. Compresseur à spirale selon l'une quelconque des revendications 1 à 8, dans lequel le compresseur à spirale est entraîné par un moteur électrique (25, 26).

10. Compresseur à spirale selon l'une quelconque des revendications 1 à 9, dans lequel la première paroi fixe (34) est formée d'un seul tenant avec l'élément formant spirale fixe (31).

11. Compresseur à spirale selon l'une quelconque des revendications 1 à 10, dans lequel le passage d'alimentation (59, 60) comprend un passage fixe (60), un renfoncement de communication (62), et un passage mobile (59), le renfoncement de communication (62) et une zone d'une ouverture (60a) du passage mobile (59) fonctionnant respectivement comme un siège de soupape (64) et comme une partie de soupape (65) pour ouvrir et fermer le passage d'alimentation (59, 60).

12. Compresseur à spirale selon la revendication 11, dans lequel le renfoncement de communication (62) et le passage mobile (59) sont continuellement en communication mutuelle.

13. Compresseur à spirale selon l'une quelconque des revendications 1 à 12, dans lequel le carter (11) définit en outre une zone de pression d'aspiration (15, 22, 51), la zone de pression d'aspiration (15, 22, 51) et la chambre de contre-pression (56) communiquant mutuellement à travers un passage de vidange (57), dans lequel un étranglement (57c) est positionné entre une ouverture (57b) du passage de vidange (57) et la zone de pression d'aspiration (12, 22, 51).

Drawing